US5876298A - Speed reduction device having overrunning clutch - Google Patents

Speed reduction device having overrunning clutch Download PDF

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Publication number
US5876298A
US5876298A US08/884,632 US88463297A US5876298A US 5876298 A US5876298 A US 5876298A US 88463297 A US88463297 A US 88463297A US 5876298 A US5876298 A US 5876298A
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United States
Prior art keywords
inner gear
gear plate
outer ring
speed reduction
teeth
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/884,632
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English (en)
Inventor
Akira Kato
Takahiro Souki
Masaru Kamiya
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Denso Corp
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Denso Corp
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Filing date
Publication date
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Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAMIYA, MASARU, KATO, AKIRA, SOUKI, TAKAHIRO
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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/108—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D2041/0646—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls the intermediate coupling members moving between recesses in an inner race and recesses in an outer race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/01—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with permanent magnets

Definitions

  • the present invention relates to a speed reduction device having an overrunning clutch and, particularly, a vehicular rotary machine which has a starting motor or a starter-generator.
  • a common starter motor for a vehicle has an overrunning clutch disposed between the pinion shaft and the driving shaft of the motor to prevent over-run of the starter motor when an engine starts and the starter motor is driven by the engine.
  • a speed reduction device is sometimes employed in the starter motor to reduce the size of the starter motor and also to increase the engine starting torque.
  • an eccentric-gear speed-reduction device which is composed of a drive shaft having an eccentric ring and an internal gear in mesh with the eccentric gear and provides a large speed reduction ratio has been proposed.
  • the present invention has an object of providing a simple speed reduction device which makes a rotary machine compact.
  • Another object of the invention is to provide a simple speed reduction device integral with an overrunning clutch having a large speed reduction ratio.
  • a speed reduction device comprises an overrunning clutch, a drive shaft having an eccentric ring, an inner gear plate disposed to be rotatable relative to the eccentric ring.
  • the gear plate has a plurality of teeth therearound and an engagement hole.
  • the device further has a fixing pin fixed to the housing in engagement with the engagement hole of the inner gear plate to restrict rotation of the inner gear plate to thereby allow swinging of the gear plate, an outer ring disposed around the inner gear plate and connected to a driven shaft and a torque transmitting member which engages one of the teeth of the inner gear plate to transmit torque from the inner gear plate to the outer ring.
  • the torque transmitting member is arranged to disengage the teeth of the inner gear plate by centrifugal force when the outer ring rotates at a speed higher than a threshold value.
  • the torque transmitting member is preferably arranged to separate from the inner gear plate completely by centrifugal force when the outer ring rotates higher than a threshold value.
  • the torque transmitting member preferably comprises an outer pin in engagement with at least one of the teeth of the inner gear plate in response to swinging operation of the inner gear plate, and the outer ring has a torque transmitting portion for holding the outer pin to be in engagement with one of the teeth of the inner gear plate and a torque interrupting portion for holding the outer pin to be separate from the teeth.
  • the speed reduction device may comprise an overrunning clutch, a housing, a drive shaft having an eccentric ring disposed eccentrically therearound; a driven shaft, an inner gear plate disposed to be rotatable relative to the eccentric ring.
  • the gear plate has a plurality of teeth therearound and a plurality of engagement holes.
  • the speed reduction device further comprises a plurality of fixing pins, each of which is fixed to the housing in engagement with one of the engagement holes of the inner gear plate, to restrict rotation of the inner gear plate to thereby allow swinging of the gear plate, an outer ring disposed around the inner gear plate and connected to the driven shaft and a torque transmitting member to engage the teeth of the inner gear plate and transmit torque from the inner gear plate to the outer ring.
  • the torque transmitting member is arranged to disengage the teeth of the inner gear plate by centrifugal force when the outer ring rotates at a speed higher than a threshold value.
  • the speed reduction device having an overrunning clutch may comprise a housing, a drive shaft having a pair of eccentric rings axially disposed eccentrically therearound, a driven shaft supported rotatably by the housing, a pair of inner gear plates disposed to be rotatable relative to the eccentric ring.
  • Each of the inner gear plates has a plurality of teeth therearound and a plurality of engagement holes, and each one of the teeth of one of the inner gear plates is disposed between adjacent teeth of the other inner gear plate.
  • the speed reduction device further comprises a plurality of fixing pins which are fixed to the housing in engagement with the engagement holes of the inner gear plates respectively to restrict rotation of the inner gear plates and allow swinging of the gear plates, an outer ring disposed around the inner gear plates and connected to the driven shaft and a torque transmitting member which is disposed on the inner surface of the outer ring to engage the teeth of the inner gear plates to transmit torque from the inner gear plates to the outer ring.
  • the torque transmitting member is arranged to disengage the teeth of the inner gear plates by centrifugal force when the outer ring rotates at a speed higher than a threshold value.
  • FIG. 1 is a schematic cross-sectional side view illustrating a starter generator for a vehicle according to a first embodiment of the present invention
  • FIG. 2 is an enlarged view illustrating a main portion of the starter generator shown in FIG. 1;
  • FIG. 3 is a cross-sectional front view of a portion shown in FIG. 2 cut along a line III--III;
  • FIG. 5 is a perspective and partially cross-sectional view illustrating a main portion shown in FIG. 2;
  • FIG. 6 is an enlarged view illustrating a main portion of a starter generator according to a second embodiment
  • FIG. 7 is a cross-sectional front view illustrating a portion shown in FIG. 6 cut along a line VII--VII;
  • FIG. 9 is a cross-sectional front view illustrating a main portion of a speed reduction section according to a third embodiment
  • FIG. 10 is a cross-sectional side view illustrating a starter for a vehicle according to a fourth embodiment
  • FIG. 11 is a cross-sectional side view illustrating a starter for a vehicle according to a fifth embodiment
  • FIGS. 12A and 12B are enlarged cross-sectional views illustrating operation of a main portion of a speed reduction section according to a sixth embodiment
  • FIG. 13 is a perspective and partially cross-sectional view illustrating a main portion of a speed reduction section according to a seventh embodiment
  • FIG. 14 is a perspective and partially cross-sectional view illustrating a main portion of a speed reduction section according to an eighth embodiment
  • FIG. 15 is a perspective and partially cross-sectional view illustrating a main portion of a speed reduction section according to a ninth embodiment
  • FIG. 16 is a perspective and partially cross-sectional view illustrating a main portion of a speed reduction section according to a tenth embodiment
  • FIG. 17 is an enlarged view illustrating a main portion of a speed reduction section according to the tenth embodiment.
  • FIG. 18 is an enlarged view illustrating a main portion of a speed reduction section according to eleventh and twelfth embodiments.
  • a speed reduction device applied to a starter-generator according to a first embodiment of the present invention is described with reference to FIGS. 1 to 5.
  • the starter-generator is composed of a generator section 1, a starter motor section 2, a speed reduction section 4 having an eccentric gear mechanism (hereinafter referred to as the eccentric gear section) and a housing 10.
  • the generator section 1 is a common AC generator or an aternator for a vehicle, the housing 10 supports a rotor 11 and a generator shaft 12 via bearings 13 and 14.
  • the rotor 11 has a pole core 110 and a field coil 111 wound around the central portion of the pole core 110.
  • the stator 15 is disposed around the rotor 11 and is composed of an armature core 150 fixed to the inner periphery of the housing 10 and an armature winding 151.
  • a voltage regulator 16, a three-phase full-wave rectifier 17 are disposed in the housing 10, and a slip ring unit 19 is fixed to the generator shaft 12.
  • the brush unit 18 supplies field current to the field coil 111 through the slip ring unit 19.
  • the front end (left end in FIG. 1) of the generator shaft 12 is connected to the crank shaft of an engine.(not shown).
  • the starter motor section 2 is a common DC starter motor and is composed of an armature 21 carried by a starter shaft 22 and a pair of bearings 23 and 24, through which the armature 21 is supported by the housing 10.
  • the starter shaft 22 is disposed in tandem and in alignment with the generator shaft 12.
  • the armature 21 is composed of an armature core 210 carried by the starter shaft 22, an armature winding 211 wound therearound and an annular commutator 222 carried by a resinous member fixed to the starter shaft 22.
  • a stator 25 is composed of a pole core 250 which is fixed to the inner periphery of the housing 10 and a field coil 251 wound around the pole core 250.
  • a brush unit 223 is fixed to the housing 10, and the armature winding 211 is supplied with current through the brush unit 223 and the commutator 222.
  • the eccentric gear section 4 is described with reference to FIGS. 2 and 3.
  • An eccentric ring 40 is fixed to the front end of the starter shaft 22 by a key 41a so that the axis thereof is eccentric to the axis of the shaft 22, and an inner gear plate 42 is fitted to a bearing 41, which is fitted to the outer periphery of the eccentric ring 40 coaxially therewith so that the inner gear plate 42 can rotate about the eccentric ring 40.
  • Gear teeth 43 are formed on the outer periphery of the inner gear plate 42, and an outer ring 44 is disposed coaxially with the inner gear plate 42 to surround the same at a certain distance.
  • the outer ring 44 is formed integrally with the rear end (right end in FIG. 2) of the generator shaft 12.
  • the outer ring 44 has a plurality of cavities 45 formed circumferentially on the inner periphery thereof at equal intervals to accommodate a plurality of cylindrical outer pins 46 one by one so as to move and rotate therein.
  • the cavities 45 are formed on the inner periphery of the outer ring 44 coaxial with the starter shaft 22.
  • the number (e.g. 26) of cavities 45 or outer pins 46 is one less than the number (e.g. 25) of the teeth 43 of the inner gear plate 42 in FIG. 3.
  • the profile of the teeth 43 of the inner gear plate 42 is shaped into an epitrochoidal-parallel curve, which is a curve parallel to a epitrochoidal curve and forms an inner envelope of a circle of the teeth having the center thereof located on the epitrochoidal curve.
  • the profile of the teeth 43 can be shaped into an involute curve.
  • the inner gear plate 42 has eight through holes 47 formed at equal intervals (at 45 degree intervals) on a circumference which is coaxial with gear plate 42, so that each of the through holes 47 movably receives an end of one of fixing pins 48 covered with one of bushes 49 extending from the housing 10.
  • each of the fixing pins 48 is press-fitted to the housing 10 so that the pins 48 are disposed at a circumference which is coaxial with the axis of the starter shaft 22 to allow the eccentric motion of the inner gear plate 42.
  • An outer periphery of each of the bushes 49 is in contact with the corresponding one of the through holes 47.
  • the outer ring 44 has an annular groove 44a formed in the inner periphery thereof to accommodate an annular garter spring 50 therein as shown in FIG. 5, which biases all the outer pins 46 radially inward.
  • the cavities 45 has a torque transmitting portion 45a, a torque interrupting portion 45b and a boundary portion 45c as shown in FIGS. 4A, 4B and 4C.
  • Each of the torque transmitting portion 45a and torque interrupting portion 4b has a cylindrical surface having the same inside diameter as the outside diameter of the outer pin 46 so as to be in close surface-contact with the outer pin 46 as shown in FIGS. 4A and 4C.
  • the torque interrupting portion 45b is located to be adjacent to the torque transmitting portion 45a at a rear side in the rotating direction (e.g. left in FIG. 4A) and radially outside the outer ring 44.
  • the boundary portion 45c is formed between the torque transmitting portion 45a and the torque interrupting portion 45b.
  • the boundary portion 45c has a suitable height and continuous curvature to allow smooth movement of the outer pin 46 between the two portions 45a and 45b.
  • the cavities 45 are filled with grease and a cover 51 is disposed to cover the outer circumference of the outer ring 44 as shown in FIG. 2.
  • the cylindrical surfaces of the torque transmitting portion 45a and the torque interrupting portion 45b can be formed larger or smaller than the diameter of the outer pin 46 as according to various circumstances. For example, larger interrupting portions 45b provide more smooth movement of the outer pins 46 to the transmitting portions 45a.
  • the eccentric gear section 4 is assembled as follows.
  • the bearing 23 and a cylindrical spacer 53 are fitted to the starter shaft 22, and the eccentric ring 40, the bearing 41 and the inner gear plate 42 are fitted successively.
  • the fixing pins 48 with the bushes 49 thereon are thereafter press-fitted to the housing 10.
  • a guide disk 54 is fitted to the front end (left in FIG. 2) of the starter shaft 22 and fastened thereto by a nut 55 so that the spacer 53 and the guide disk 54 restrict axial movement of the eccentric ring 40.
  • the inner gear plate 42 is positioned between the guide disk 54 and the housing 10 at small clearances.
  • the eccentric ring 40 is rotated to swing the inner gear plate 42 in cooperation with the fixing pins 48, which restrict rotation of the inner gear 42.
  • the inner gear plate 42 swings eccentrically one time so that the outer pins 46 are driven by the teeth of the inner gear plate 42 clockwise.
  • the outer ring 44 rotates clockwise by an interval between the adjacent cavities 45.
  • a combination of the twenty five (25) teeth of inner gear plate 42 and the twenty six (26) outer pins provides the speed reduction ratio of 1/26.
  • the outer ring 44 When an engine starts and the engine rotation speed becomes higher, the outer ring 44 is rotated clockwise. When the rotation speed of the outer ring 44 becomes higher than the swing speed of the teeth 43 of the inner gear 42, the outer pin 46 is brought into contact with an edge 45d of the torque interrupting portion 45b as shown in FIG. 4B. Then, the outer pin 46 gets on one of the teeth 43, lifts up the garter spring 50 and gets deeper in the interrupting portion 45b, thereby disengaging from the teeth 43. As a result, the outer ring 44 runs idle around the inner gear plate 42, and the torque from the starter shaft 22 is not transmitted to the generator shaft 12.
  • the centrifugal force applied to the outer pins 46 becomes stronger than the biasing force of the garter spring 50, and the outer pins 46 overwhelm the garter spring 50 and always remain in the torque interrupting portions 45b as shown in FIG. 4C, thereby separating the outer ring 44 from the inner gear plate 42.
  • the set speed is higher than the engine starting speed and lower than the engine idling speed.
  • a starter generator according to a second embodiment of the present invention is described with reference to FIGS. 6-8.
  • the eccentric gear section 4 of the first embodiment is only replaced with an eccentric gear section 4a in this embodiment.
  • the eccentric gear section 4a is composed of a pair of first and second inner gear plates 42a and 42b, each of which is disposed to swing independently.
  • the first inner gear plate 42a is fitted to the starter shaft 22 through a first eccentric ring 40a and a bearing 41a
  • the second inner gear plate 42b is fitted to the starter shaft 22 through a second eccentric ring 40b and a bearing 41b.
  • the first and second inner gear plates 42a and 42b have, respectively, through holes 47a and 47b similar to those of the first embodiment which receive jointly the fixing pins 48, so that the rotation of the gear plates 42a and 42b is restricted by the fixing pins 48.
  • the first and second inner gear plates 42a and 42b have teeth 43a and 43b respectively, which are in mesh with the outer pins 46 respectively.
  • the eccentric rings 40a and 40b are disposed to be eccentric to opposite directions (180 degree in angle).
  • each of the outer pins 46 is pushed by either one of the teeth 43a and 43b against the outer ring 44, so that the operation of the outer pins 46 becomes smoother than the operation of the same in the first embodiment, thereby decreasing torque fluctuation, vibration and noises.
  • the angular position of the center of the torque transmitted from the first inner gear plate 42a to the outer ring 44 and the angular position of the center of the torque transmitted from the second inner gear plate 42b to the outer ring 44 are located to be opposite with regard to the axis of the starter shaft 22, the outer ring 44 operates smoothly without unbalance force.
  • a starter generator according to a third embodiment is described with reference to FIG. 9.
  • the eccentric gear section 4c of this embodiment has a half as many outer pins 46 and cavities 45 as the eccentric gear section of the second embodiment, thereby making the gear section simpler.
  • a starter according to a fourth embodiment is described with reference to FIG. 10.
  • the generator section 1 of the first embodiment is omitted.
  • the shaft 12 is connected to the engine crank shaft through a torque transmitting means (e.g. pulleys and a belt).
  • a starter with an eccentric gear section according to a fifth embodiment is described with reference to FIG. 11.
  • the generator section 1 of the second embodiment is omitted, and the shaft 12 is connected to the engine crank shaft through a torque transmitting means (e.g. pulleys and a belt).
  • a torque transmitting means e.g. pulleys and a belt
  • a speed reduction section 4 according to a sixth embodiment of the present invention is described with reference to FIGS. 12A and 12B.
  • the garter spring 50 of the first embodiment is replaced with coil springs disposed in each one of the cavities 45.
  • a cylindrical hole is formed in each one of the torque interrupting portions 45b to hold a part of the spring 5.
  • the coil springs 5 bias the outer pins 46 against the torque transmitting portions 45b as shown in FIG. 12A.
  • a speed reduction section according to a seventh embodiment of the present invention is described with reference to FIG. 13.
  • a plate member made of permanent magnet material is used for the inner gear plate 42 in this embodiment.
  • the outer surfaces of the teeth 43 are magnetized in the axial direction to form N poles 7 and S poles 8 thereon.
  • the outer pins 46 are made of soft magnetic member. Accordingly, the outer pins 46 are attracted by the teeth 43 and fitted to portions between the teeth 43 and normally engage the torque transmitting portions 45a.
  • the outer pins 46 are operated in the same manner as the previous embodiments. That is, the centrifugal force applied to the outer pins 46 overwhelms the magnetic force of the teeth surfaces and get in the torque interrupting portions 45b when the engine speed becomes higher than a set speed.
  • the outer ring 44 can be either magnetic or nonmagnetic.
  • This structure eliminates mechanical friction of the garter spring or coil springs.
  • a speed reduction section according to an eighth embodiment is described with reference to FIG. 14.
  • the speed reduction section according to the eighth embodiment has outer pins 46 made of permanent magnet material.
  • the outer pins 46 are magnetized in the axial direction.
  • the inner gear plate 42 is made of soft magnetic material, and the outer ring 44 is made of nonmagnetic material. The operation of the outer pins are almost the same as the seventh embodiment.
  • a speed reduction section according to a ninth embodiment is described with reference to FIG. 15.
  • the inner gear plate 42 and the outer pins 46 are made of permanent magnet material, and the teeth 43 are magnetized in a direction opposite to that of the outer pins 46 so that each one of the teeth 43 and corresponding one of the outer pins 46 are attracted more strongly than the corresponding members in the eighth embodiment.
  • the outer ring 44 is made of nonmagnetic material. The operation of the outer pins are almost the same as the eighth embodiment.
  • a speed reduction section according to a tenth embodiment is described with reference to FIGS. 16 and 17.
  • the outer pins 46, the inner gear plate 42 and the outer ring 44 are made of permanent magnet material and magnetized as shown in FIGS. 16 and 17.
  • the torque transmitting portion 45a is magnetized in the direction opposite to the magnetized direction of the outer pins 46, and the torque interrupting portion 45b is magnetized in the direction same as the magnetized direction of the outer pins 46. Therefore, the torque transmitting portions 45a attract the outer pins 46 and the torque interrupting portions 45b repulse the outer pins 46.
  • a speed reduction section according to an eleventh embodiment is described with reference to FIG. 18.
  • the inner gear plate 42 and the outer ring 44 are made of permanent magnet material, and the outer pins are made of soft magnetic material.
  • the outer ring 44 is magnetized in the axial direction to form S pole at one end, and the inner gear plate 42 is magnetized in the axial direction to form N pole at the same end as the outer ring 44 as shown in FIG. 18.
  • the outer pin 46 bridges the S-pole of the torque transmitting portion 45a of the outer ring 44 and the N-pole of the teeth surface of the inner gear plate 42 so that the outer pin 46 can engage the torque transmitting portion 45a surely.
  • a speed reduction section according to a twelfth embodiment is described with reference to FIG. 18.
  • the inner gear plate 42, outer ring 44 and outer pin 46 are made of soft magnetic material, which are magnetized by an outside magnetic field, such as a permanent magnet or a magnetic coil, to polarize the outer periphery of the inner gear plate to become S-pole and the inner periphery of the outer ring 44 to become N-pole.
  • the field coil 111 and the generator shaft 12 can be utilized as a part of the outside magnetic field.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Retarders (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
US08/884,632 1996-07-10 1997-06-27 Speed reduction device having overrunning clutch Expired - Fee Related US5876298A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP8-180806 1996-07-10
JP18080696A JP3763166B2 (ja) 1996-07-10 1996-07-10 減速装置

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US08/884,632 Expired - Fee Related US5876298A (en) 1996-07-10 1997-06-27 Speed reduction device having overrunning clutch

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JP (1) JP3763166B2 (ja)
DE (1) DE19729620B4 (ja)

Cited By (27)

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US6232694B1 (en) * 1999-07-01 2001-05-15 John Leslie Starter generator with slots in the commutator head assembly
US20010033113A1 (en) * 2000-04-10 2001-10-25 Tadashi Takano Rotating electrical machine
US6453772B1 (en) * 1998-11-05 2002-09-24 Robert Bosch Gmbh Eccentric toothed gearing
US6491601B1 (en) * 1999-03-12 2002-12-10 Robert Bosch Gmbh Eccentric toothed gearing
EP1300602A3 (en) * 2001-10-02 2003-06-04 Koyo Seiko Co., Ltd. Pulley unit having one-way clutch
US20040023754A1 (en) * 2000-09-08 2004-02-05 Flugrad Jr. Donald R. Self-actuating, traction-drive speed changer
US20040207276A1 (en) * 2003-04-21 2004-10-21 Eugene Chiappe Clutched starter motor assembly for aircraft piston
US20060173419A1 (en) * 2005-02-02 2006-08-03 Malcolm David R Medical fluid delivery system and method relating to the same
US20060196306A1 (en) * 2003-04-04 2006-09-07 Hammerbeck John P Ratio changing method and appartus
US20070029893A1 (en) * 2004-04-15 2007-02-08 Keiper Gmbh & Co. Kg Adjuster for a vehicle seat
US20070060433A1 (en) * 2004-04-15 2007-03-15 Keiper Gmbh & Co. Kg Drive unit of an adjuster in a vehicle
US20070096050A1 (en) * 2005-10-31 2007-05-03 Dan Jones Valve actuator
US20070171319A1 (en) * 2006-01-26 2007-07-26 Sanyo Epson Imaging Devices Corporation Liquid crystal apparatus and electronic device
US20080146394A1 (en) * 2005-08-23 2008-06-19 Keiper Gmbh & Co. Kg Gear stage
US20080176701A1 (en) * 2007-01-22 2008-07-24 Sumitomo Heavy Industries, Ltd. Geared motor reducer and geared motor
CN102684376A (zh) * 2012-05-14 2012-09-19 周峰 一种用于低启动电流电动机的重力离心磁性离合器
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CN102684374A (zh) * 2012-05-14 2012-09-19 周峰 一种重力离心磁性离合器与行星减速机构的连接结构
US20120283063A1 (en) * 2008-06-13 2012-11-08 Frieder Krueger Adjustment fitting
CN103238004A (zh) * 2010-11-30 2013-08-07 谢夫勒科技股份两合公司 自由轮和用于具有自由轮的内燃机的起动装置
CN104132079A (zh) * 2014-01-23 2014-11-05 深圳市超越传动科技有限公司 弧面偏心块式超越离合器
CN105378230A (zh) * 2013-07-10 2016-03-02 伊斯帕诺-絮扎公司 飞机涡轮发动机的附件齿轮箱的紧凑结构
CN106545597A (zh) * 2016-12-21 2017-03-29 宁波市镇海捷登应用技术研究所 一种能延长使用寿命的超越离合器
CN107448505A (zh) * 2017-08-02 2017-12-08 汤树人 一种无控高速触发且可低速保持的离合器
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CN103238004B (zh) * 2010-11-30 2016-04-20 舍弗勒技术股份两合公司 自由轮和用于具有自由轮的内燃机的起动装置
CN102678784B (zh) * 2012-05-14 2014-04-02 周峰 一种用于重力离心磁性离合器的从动轮
CN102678784A (zh) * 2012-05-14 2012-09-19 周峰 一种用于重力离心磁性离合器的从动轮
CN102684374A (zh) * 2012-05-14 2012-09-19 周峰 一种重力离心磁性离合器与行星减速机构的连接结构
CN102684376A (zh) * 2012-05-14 2012-09-19 周峰 一种用于低启动电流电动机的重力离心磁性离合器
CN102684373B (zh) * 2012-05-14 2014-01-15 周峰 一种低启动电流电动机
CN102684373A (zh) * 2012-05-14 2012-09-19 周峰 一种低启动电流电动机
CN105378230B (zh) * 2013-07-10 2017-04-26 伊斯帕诺-絮扎公司 飞机涡轮发动机的附件齿轮箱的紧凑结构
CN105378230A (zh) * 2013-07-10 2016-03-02 伊斯帕诺-絮扎公司 飞机涡轮发动机的附件齿轮箱的紧凑结构
US10323576B2 (en) 2013-07-10 2019-06-18 Safran Transmission Systems Compact structure for accessory gearbox of an aircraft turbine engine
RU2674299C2 (ru) * 2013-07-10 2018-12-06 Испано Сюиза Компактная конструкция вспомогательной коробки передач газотурбинного двигателя летательного аппарата
CN104132079A (zh) * 2014-01-23 2014-11-05 深圳市超越传动科技有限公司 弧面偏心块式超越离合器
CN104132079B (zh) * 2014-01-23 2016-09-07 深圳市超越传动科技有限公司 弧面偏心块式超越离合器
US10385933B2 (en) * 2015-08-29 2019-08-20 Borgwarner Inc. Freewheel and freewheel arrangement comprising such a freewheel
CN106545597A (zh) * 2016-12-21 2017-03-29 宁波市镇海捷登应用技术研究所 一种能延长使用寿命的超越离合器
CN107448505A (zh) * 2017-08-02 2017-12-08 汤树人 一种无控高速触发且可低速保持的离合器
CN110890823A (zh) * 2019-11-26 2020-03-17 常州市多维电器有限公司 一种电机及驱动助力系统

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DE19729620B4 (de) 2006-03-02
JPH1028352A (ja) 1998-01-27
JP3763166B2 (ja) 2006-04-05

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